Split antifriction-bearing construction

ABSTRACT

A method for fabricating a bearing structure of the split-ring type is described. The bearing outer race ring, after formation and hardening, is split to define a seam, and the fractured ends are separated to preassemble the bearing with antifriction elements and an inner race ring. The fractured ends are then joined by fusion-welding at the seam with an electron beam. In one method, the beam is directed axially at a radially outer portion of the seam, and in another method the beam is directed radially inwardly at the periphery, to effectively fuse the outer peripheral portions of the fractured ends to one another. In both methods, the fusion-welding is sufficiently localized to leave intact the original finish and heat treatment of the fractured ring.

United States Patent Inventor Steven T. Martin West Hartford, Conn.

Appl. No. 870,929

Filed Oct. 29, 1969 Patented July 13, 1971 Assignee Textron Inc.

Providence, 1L1.

Dlvidonofser. No. 741,731, July 1,1968.

SPLIT AN'I'IFRIC'I'ION-BEARING CONSTRUCTION 6 Claims, 7 Drawing Figs.

Primary ExaminerFrank Susko Attorney-Sandoe, Hopgood and Calimafde ABSTRACT: A method for fabricating a bearing structure of the split-ring type is described. The bearing outer race ring, after formation and hardening, is split to define a seam, and the fractured ends are separated to preassemble the bearing with antifriction elements and an inner race ring. The fractured ends are then joined by fusion-welding at the seam with an electron beam. in one method, the beam is directed axially at a radially outer portion of the seam, and in another method the beam is directed radially inwardly at the periphery, to effectively fuse the outer peripheral portions of the fractured ends to one another. In both methods, the fusiomwelding is sufficiently localized to leave intact the original finish and heat treatment of the fractured ring.

PAIENIEG .511 1 3 cm INVENT Jm mr BY panda 004 7- ATTORNEYS SPLIT ANTIFRICTION-BEARING CONSTRUCTION This application is a division of my'copending application, Ser. No. 74I,73l,filed July 1, I968.

This invention relates to a method for making bearing structures. More specifically, it relates to a method of making socalled divisible or split-bearing structures wherein the outer race ring is divisible or split during assembly for inserting more than the usual complement of antifriction elements between the inner and outer race rings of the bearing.

Patents have been granted which describe bearing structures of the divisible types; see, for instance, the patents to Pierce 1,498,748 and l,675,728, and Stearns 2,648,578 and 2,657,l$.

In a bearing structure in which the outer race ring has been fractured to permit insertion of the antifriction elements, care must be taken to maintain the broken ends in intimate interlocking mating relationship under all conditions in which the bearing may be used. In this respect, reliance upon the natural resiliency of the fractured ring is inadequate, in that support of rolling elements under load is not uniform. It has been suggested that a locking member be used on the outer race ring to maintain interlocking of the fractured ends. However, this member involves the addition of a part, the machining of a recess to receive the member in the ring, and adds undesirable weight to the bearing.

It is therefore an object of this invention to provide an improved method for assemblinga divisible bearing structure.

It is a further object of this invention to provide a divisible bearing structure capable of absorbing radial and axial loads without separation of the bearing structure.

It is still further an object of this invention to provide a method for making a lightweight bearing structure of the divisible type in an economical manner.

A specific object is to produce animproved ball bearing with a relatively full complement of balls, and without imposing limitations as to race-groove depth and effective continuity of raceway side-shoulder support.

Another specific object is to provide an improved bearing construction and method of the character indicated, wherein the bearing itselfimposes no requirement of close fit to a shaft or housing. and wherein the ability to sustain thrust loads is not impaired by sidewall discontinuities such as filling slots.

These and other objects are accomplished by my invention which will be described in conjunction with the accompanying drawings. In said drawings:

FIG. I is a fragmentary view inside elevation of a preassembled bearing structure with a split outer race ring, prior to welding in accordance with my invention;

FIG. 2 is a perspective view of a hardened and finished outer race ring prior to fracture;

FIG. 3 is a simplified side view, illustrating the step of fracturing the outer race ring;

FIG. 4 is an enlarged cross-sectional view of the bearing taken along the line 4-4 of FIG. I;

FIG. 5 is a fragmentary view in perspective to show one method of fusion-welding the radially outer portion of the fracture in accordance with my invention;

FIG. 6 is a view similar to FIG. 5 to show an alternate method for fusion-welding the fractured ring ends to one another; and

FIG. 7 is an enlarged perspective fragmentary view of a sectionof the outer ring of FIG. 2, taken along a central radial plane of the raceway.

Briefly, my invention contemplates the fracturing of a hardened outer race ring of a bearing, followed by assembly with the inner race ring and the antifriction elements including a retainer, if needed), and subsequent fusiomjoining the fractured ends of the outer race-ring. with insignificant impairment of prior heat treatment or finish of the race surface;

In FIG. 1. s preassembled bearing structure 10 is partially shown with an inner hardenedu'ace ring 16, a hardenedsplit outer race ring 12 and antifriction elements I4, such as balls.

inserted between the rings. The inner and outer race rings are provided respectively with concave races 11 and 13 for the elements 14. The outer race ring 12 is provided at its outer surface with a groove 18 which runs lengthwise of the ring axis and preferably parallel thereto. The outer ring is split along the seam 20 which commences at the bottom of the groove and terminates at the inner surface of the ring. The seam 20 is formed by the adjacent mating fractured ends 22 and 24 and extends axially throughout the ring to permit enlargement of the ring for the insertion of a complement of balls between the rings.

The outer race ring 12 as shown in FIG. 2 is formed of tubular stock, bar stock or a forging, in the usual manner. The ring is machined to its final dimensions both inside and outside and provided with a raceway 13. The narrow groove 18 is formed as part of the machining. The groove may be U-shaped or V- shaped but is shown square, and extends longitudinally of the ring. The purpose of this groove on the outside of the ring 12 is to provide a locally weakened section for fracture along a preselected generally radial seam.

The groove l8, may be out before or after hardening, but I prefer the latter alternative. Hardening may be accomplished by the customary heat-treating methods. The ultimate degree of hardness is immaterial except that it should permit the subsequent fracturing without permanent deformation of the ring.

The ring may be casehardened by hardening the race surface to a preselected depth with the majority of the ring material retained at a lower hardness level but with high strength. The casehardened ring must be capable of being fractured without permanent deformation.

After the ring is hardened, its raceway 13 is ground and finished to the desired ultimate finish. Ring 12 is then broken along a radial seam or plane of weakness as determined by the groove 18. With the ring 12 supported on a suitable table surface 9, a radially inward breaking force or squeeze F is applied as shown in FIG. 3 by, for instance, a loading member 26 positioned directly over the groove [8. The force F is carefully controlled to avoid injury of the broken surfaces and to avoid any permanent deformation. Under the force F, the vertical compression of ring 12 produces horizontally outward displacements D,D at ring portions intermediate the squeezed regions, resulting in fracture due to localized severe tension and bending stress in the ring at groove 18. Upon release of force F, the facing surfaces of the fractured ring ends 22 and 24 assume a mated relation to from a near-perfect cylinder having a smooth raceway 13 for the bearing antifriction elements.

After fracture. the outer race ring 12 is ready to be preassembled with the other parts of the bearing parts into a bearing unit. Insertion of the ball elements 14 may be done for instance as shown in the patent to Gurney 845,632. Although in this patent a full complement of balls is shown inserted between the race rings, a lesser number of balls WlLll a suitable retainer or cage (suggested at 21) may be used. The number of antifriction elements is dependent upon the load requirements for the bearing. T

The cross-sectional view of FIG. 4 illustrates the relation of the presssembled parts, taken in the general plane of fracture, to reveal the face of the fractured end 24. The antifriction elements [4 are seen to be received in deep races 1l-l3 defined between substantial shoulders 17-19 and 15-21 on the respective rings 12-46.

Because the bearing structure of FIG. I may not be adequately held together by the inherent resilience of the ring 12. an additional step is performed to join the ends 21 and 24 to one another; preferably, however, and in order to assure perfect fit and continuity of the raceway, the ring 12 is held in s'suitable circumferentially confining clamp, jig, or other forture (not shown) during the joining step. This joining step is preferably carried out by controllably fusing portions of these ends by a very quick and therefore very localised heating process.

More specifically, in the method of FIG. 5, the structure of FIG. 1 is fusion-joined by an energized beam of charged particles 30, such as an electron beam, directed and focused at an outer portion of the scam 20, as at a radially outwardly local ized area of an axial end face of ring [2, indicated generally by the dotted line 34. The energized beam is directed substantially parallel to the bearing axis, and its power and power density so controlled that the axial zone, i.c., axially inwardly of the localized surface area 34, is quickly melted along the fractured seam 20. This zone may be, as shown, confined to the material immediately adjacent the bottom of the groove and the seam 20. Upon removal ofthc beam 30, the fused material coalesccs to form a welded junction of the fractured ends 22 l 24. The fusion is controlled to occur so quickly that neither the surfacehardened condition nor the ground finish of the nearby raceway 13 is adversely affected or deteriorated; moreover, the weld is achieved without affecting any of the other preassembled bearing parts.

Alternatively, the fusion-joining may be done by directing the beam 30 first at one axial end face of the seam to fused a radially outwardly localized area to a preselected axial depth. The depth may be limited to a surface tack-type weld or extend axially along the seam, depending upon the desired amount of metal to be fused by the beam. Such depth control may be simply obtained by varying the focus and power of the beam. After fusion at one axial end, the opposite axial end of the scam may be so fused. An advantage of this welding method resides in the accompanying reduction of the radially extending heat-affected zone, thereby avoiding a change in the finish and hardness of the nearby raceway.

Furthermore, the beam 30 may be directed radially inwardly at the seam to fuse the outer periphery thereof. This may be done during a traverse of the beam along the axial length of the seam, or with a stitching-type beam with overlapping or spaced stitches. The stitched weld may simply be carried out by pulsing the beam. Pulsing of the beam provides a convenient method for controlling the fusion depth and the heat-affected zone in the ring. FIG. 7 shows the orientation of the ring 12 relative to the beam and the stitched welds 7 and 8.

As shown in FIG. 7, the fusion zone 34 terminates radially inwardly a significant distance from the hardened raceway 13. This permits retention of the raceway hardness and reduces distortions of the seam in the raceway.

An important advantage of the fusion-welding step as described is its ability to control the circumferential shrinkage of the outer race ring. Too much shrinkage, produced by an excessive amount of fused metal, will create excessive stresses in the ring, whereas the correct amount will advantageously compress the fractured ends 2224 together to assure the desired smooth raceway 13. The beam focus can be accurately controlled to provide the desired size of the melted zone. For instance, a beam used to melt zone 34 may be 0.030 inch thick and can easily be adjusted to melt at smaller zone 32 with a beam size of 0.0l0 inch. With such latter sized beam the amount of fused metal and heat-affected zone can be significantly reduced.

With the beam oriented as shown in FIG. 5, i.e., parallel to the bearing axis, inadvertent beam damage to other bearing parts may be avoided. However, the situation may arise where the amount of fused metal must be reduced to a minimum or where the heat from the beam-melted zone is to be kept as distant from the hardened raceway 13 as possible. FIG. 6 shows an alternate method for fusion-joining the fractured ends 22-24.

ln FIG. 6 the outer race ring is again provided with a weakening groove. However, the groove 18 is this case is preferably formed during the formation of the ring by passing a drill adjacent the outer periphery of the ring and parallel to the ring axis with the drill partially breaking through the ouysr surface. The groove thus formed localizes ring weakness, or fracturing purposes; it is also characterized by opposed p|ojecting outer edges 36 and 38 facing one another across the groove. The ring is hardened, finished and fractured as hereto fore described.

The facing edges 3638 are formed to allow the severed peripheral portions of the ring 12 to be effectively connected to one another. Since the edges are separated from one another by a gap, a metallic insert 40 is formed to fit within the groove 18. The insert is generally cylindrically shaped and is provided with a fiat 4], to prevent protrusion of the insert outside the periphery of the ring. The insert has a diameter which is smaller than the diameter of the groove but greater than the gap separating the edges 36-38.

The insert diameter is selected to provide a convenient method for controlling the effect which the circumferential shrinkage force, due to fusion-welding, has on the scam 20. By suitably controlling the difference in diameter between the insort and the groove to be less than the circumferential shrinkage, the insert is made to absorb a portion of the force, thereby assuring firm mating of the fracturedends without distortions appearing at the scam in the raceway. This control may also be obtained by applying a longitudinal taper to the insertv The tapered insert then has the shape of a truncated cone.

By suitable fixturing, the insert 40 is held within the groove in abutment with the radially inward facing sides of the edges. A beam of charged particles is then directly radially inwardly generally at the insert and sufficiently defocuscd to melt the edges 3638 along the zone 42-44, as well as to melt por tions ofthc insert.

Upon removal of the beam the melted material solidifies and the fractured ends 22-24 are effectively connected to one another. The melted zone is now considerably further from the hardened raceway 13 so that very little heat will reach this part of the ring. The smaller diameter of the insert will not impede the closing of the seam 20. If desired, one may, be carefully machining the diameter of the insert, prevent excessive stresses within the ring by providing a close fit of the insert in the groove.

Other welding methods may be employed to interconnect the outer edges 42-44 to the insert. For instance, a resistance welding operation may be conveniently carried out since the direction of current flow may be carefully controlled. One electrode may be coupled to the insert and the other to both outer edges.

It will be seen that I have described an improved high-com plement antifriction construction having inherent ability to retain its dimensions under extended high load use. The invention achieves desirable results of accurately maintaining, in close, permanent, mated relation, the severed adjacent parts of a heat-treated, finish ground raceway that has been locally severed. The welding by which this relation is maintained is 10- calized at a radius sufficiently remote from the race surface to have no deleterious effect on the prior race surface heat treatment, and permanent retention of the reunited ring is assured. The method of the invention makes possible the manufacture of ball bearings of high load capacity, particularly for high thrust load applications, because a high complement of balls may be accommodated in races having deep race shoulders, uninterrupted by filling slots, and a united continuous outerring hoop permanently retains and supports the fracture of the outer race.

What 1 claim is:

l. A ball bearing comprising hardened inner and outer rings having radially opposed raceways and a plurality of balls riding said raceways and concentrically retaining said rings, said raceways being defined by continuous lateral shoulders and the number of balls in said plurality exceeding the maximum number which can be inserted by eccentric positioning of said rings during ball-insertion, said outer ring having at one angular location a local longitudinal fracture defining circumferentially adjacent abutting ends at the fracture seam, and a fusion-welded interconnection of said ends within the body of said outer ring and at a location external to the raceway at the seam.

2. A ball bearing according to claim 1, in which said interconnection is tensed against the reacting compressional abutment of the unwelded portions of said ends at the seam, whereby the fracture at the raceway surface is compresF sionally retained by said interconnection.

3. An antifriction bearing comprising hardened inner and outer rings having radially opposed raoeways and a plurality of antifriction elements riding said raceways and concentrically positioning said rings, said raceways being defined between continuous lateral shoulders and the number of elements in said plurality exceeding the maximum number which can be inserted by eccentric positioning of said rings during elementinsertion, said outer ring having at one angular location a local longitudinal fracture defining circumferentially adjacent abutting ends at the fracture seam, and a fusion-welded interconnection of said ends within the body of said outer ring and at a location external to the raceway at the seam.

4. A bearing according to claim 3, in which said interconnection is axially external to the raceway at the seam.

5. A bearing according to claim 3, in which said interconnection is radially external to the raceway at the seam.

6. A bearing according to claim 3, in which said interconnection is both radially and axially external to the raceway at the seam.

I0 I 050 M09 

1. A ball bearing comprising hardened inner and outer rings having radially opposed raceways and a plurality of balls riding said raceways and concentrically retaining said rings, said raceways being defined by continuous lateral shoulders and the number of balls in said plurality exceeding the maximum number which can be inserted by eccentric positioning of said rings during ball-insertion, said outer ring having at one angular location a local longitudinal fracture defining circumferentially adjacent abutting ends at the fracture seam, and a fusion-welded interconnection of said ends within the body of said outer ring and at a location external to the raceway at the seam.
 2. A ball bearing according to claim 1, in which said interconnection is tensed against the reacting compressional abutment of the unwelded portions of said ends at the seam, whereby the fracture at the raceway surface is compressionally retained by said interconnection.
 3. An antifriction bearing comprising hardened inner and outer rings having radially opposed raceways and a plurality of antifriction elements riding said raceways and concentrically positioning said rings, said raceways being defined between continuous lateral shoulders and the number of elements in said plurality exceeding the maximum number which can be inserted by eccentric positioning of said rings during element-insertion, said outer ring having at one angular location a local longitudinal fracture defining circumferentially adjacent abutting ends at the fracture seam, and a fusion-welded interconnection of said ends within the body of said outer ring and at a location external to the raceway at the seam.
 4. A bearing according to claim 3, in which said interconnection is axially external to the raceway at the seam.
 5. A bearing according to claim 3, in which said interconnection is radially external to the raceway at the seam.
 6. A bearing according to claim 3, in which said interconnection is both radially and axially external to the raceway at the seam. 